CN115989803A

CN115989803A - Double-bearing reel

Info

Publication number: CN115989803A
Application number: CN202211271652.XA
Authority: CN
Inventors: 森成秀; 原口仁志
Original assignee: Shimano Inc
Current assignee: Shimano Inc
Priority date: 2021-10-18
Filing date: 2022-10-18
Publication date: 2023-04-21
Also published as: JP2023060526A; KR20230055348A; TW202316959A

Abstract

The invention can miniaturize a dual-bearing reel in the axial direction. A dual-bearing reel is configured such that rotation of a handle is transmitted to a spool (30) via a planetary gear (60), a clutch for switching on/off the transmission is provided, a spool shaft (31) of the spool (30) has a clutch pin (51), the planetary gear (60) has a gear portion (65) and an engagement groove (64), the gear portion (65) has a tooth portion on the outer periphery, the engagement groove (64) engages with the clutch pin (51) in an on state of the clutch in which rotation of the handle is transmitted to the spool (30), and at least a part of the gear portion (65) and the engagement groove (64) overlap in the spool axial direction (X).

Description

Double-bearing reel

Technical Field

The present invention relates to a dual bearing reel.

Background

The following dual-bearing reel is known as a conventional dual-bearing reel: the rotation of the handle is transmitted to the spool via the planetary gear, and a clutch for switching on/off of the transmission is provided (for example, refer to patent document 1).

In the case of the above-described dual-bearing reel, there is a dual-bearing reel provided with a clutch pin that is provided so as to protrude radially outward from the spool of the spool by switching operation of the clutch to an engaged position in which the clutch pin rotates in conjunction with the planetary gear and a disengaged position in which the clutch pin is disengaged from the planetary gear. When the clutch pin is provided, an inclined portion for guiding the clutch pin to an engagement position of the planetary gear is provided (for example, refer to patent document 2).

Patent document 1: japanese patent application laid-open No. 2012-100624.

Patent document 2: japanese patent application laid-open No. 2008-125467.

In such a conventional dual-bearing reel, as shown in fig. 7, since the tooth portion 101 provided on the outer periphery of the planetary gear 100 and the engaged portion 102 to which the clutch pin is engaged are disposed so as to be separated in the spool axial direction 103, there is a problem in that the dual-bearing reel is limited to be miniaturized in the axial direction.

In order to machine the inclined portion 104 guided to the engaged portion 102 as in patent document 2, the side surface of the end mill is machined so as to avoid interference of the tool with the tooth portion 101. Therefore, the engagement portion of the clutch pin including the inclined portion 104 needs to protrude longer in the spool axial direction than the planetary gear, and it is difficult to miniaturize the dual-bearing reel in the axial direction, leaving room for improvement in this respect.

Disclosure of Invention

The present invention has been made in consideration of such circumstances, and an object thereof is to provide a dual-bearing reel capable of miniaturizing the dual-bearing reel in the axial direction.

(1) The dual-bearing reel according to the present invention is a dual-bearing reel in which rotation of a handle is transmitted to a spool via a planetary gear, and a clutch for switching on/off of the transmission is provided, wherein a spool shaft of the spool has an engaging portion, the planetary gear has a gear portion and an engaged portion, the gear portion has a tooth portion on an outer periphery, the engaged portion engages with the engaging portion in an on state of the clutch in which rotation of the handle is transmitted to the spool, and at least a part of the tooth portion and the engaged portion overlap in the spool shaft direction.

According to the dual-bearing reel of the present invention, at least a part of the engagement portion engages with the engaged portion in a state of overlapping the planetary gear in the spool axial direction, so that the dual-bearing reel can be miniaturized in the spool axial direction.

Further, in the present invention, since the engaged portion is disposed in the gear portion of the planetary gear, the end mill can be processed not by the processing of the side surface of the end mill but by the end of the end mill, and therefore, a portion extending long in the axial direction of the spool as in the prior art is not required, and the dual-bearing reel can be miniaturized in the axial direction of the spool.

(2) Preferably, the engagement portion is a clutch pin protruding radially outward from a spool shaft of the spool.

In this case, at least a part of the planetary gear is engaged with the engaged portion in a state of overlapping in the spool axial direction, so that the spool can be miniaturized in the axial direction as a dual-bearing reel.

(3) The dual bearing reel may be characterized in that a recess recessed in the spool axial direction is formed in a central portion of the gear portion on the radial inner side, and the engaged portion for engaging the clutch pin is provided in the recess.

In this case, since the clutch pin engages with the engaged portion provided in the concave portion of the gear portion, the overlapping amount of the tooth portion and the engaged portion in the spool axial direction can be increased, and the dual-bearing reel can be more reliably miniaturized.

(4) The dual-bearing reel may be characterized in that a stepped portion is formed in the recessed portion along a circumferential direction around the spool shaft, and the engaged portion having a groove shape is provided at a lowermost position of the stepped portion.

In this case, since the stepped portion is provided in the gear portion of the planetary gear, the clutch pin can be guided to the engaged portion, that is, the engaged position by the stepped portion to be engaged.

In the present invention, the stepped portion enables machining by the tip portion of the end mill.

(5) The dual bearing reel may be configured such that the clutch pin has a circular cross section, and the step portion has a smaller width in the circumferential direction than the radius of the cross section of the clutch pin at a center-side end portion in the radial direction perpendicular to the spool shaft.

In this case, since the width dimension of the center-side end portion of the stepped portion is narrowed, the clutch pin temporarily moved to the stepped portion is not left in the stepped portion and is easily dropped from the stepped portion into the engaged portion. That is, in this case, the clutch pin can be reliably guided to the engaged portion.

Effects of the invention

According to the dual-bearing reel of the present invention, the dual-bearing reel can be miniaturized in the axial direction.

Drawings

Fig. 1 is a perspective view showing the overall structure of a dual-bearing reel according to an embodiment of the present invention.

Fig. 2 is a sectional view taken along line XI-XI shown in fig. 1, and is a sectional view of the dual bearing reel.

Fig. 3 is a perspective view showing a partial fracture of the structure of the planetary gear.

Fig. 4 is a perspective view of the planetary gear.

Fig. 5 is a plan view of the 1 st end of the planetary gear as seen from the spool axial direction.

Fig. 6 is a view taken along line XII-XII shown in fig. 3.

Fig. 7 is a perspective view showing the structure of a conventional planetary gear.

Detailed Description

Hereinafter, embodiments of a dual bearing reel according to the present invention will be described with reference to the accompanying drawings. In each drawing, the scale of each component may be changed as needed so that each component can be visually checked.

< integral Structure >)

As shown in fig. 1, the dual bearing reel 1 for fishing of the present embodiment includes a reel body 10, a handle 20 for rotating a spool disposed on a side of the reel body 10, and a star drag 3 disposed on a side of the reel body 10 of the handle 20. The reel 30, which is rotatably mounted on the reel body 10 and which is configured to reel out the fishing line, is rotatably mounted. The reel body 10 is attached to a fishing rod via a rod attachment portion 18.

Here, the "right-left direction" described below refers to the right-left direction when the fishing rod provided with the dual-bearing reel 1 is held and viewed from the user during fishing. In the present embodiment, the handle 20 is located on the right side of the reel body 10.

< handle >)

The handle 20 includes a crank arm 21 and a handle grip 22, the crank arm 21 is non-rotatably attached to a distal end 41a of a drive gear shaft 41 (described later) protruding to the right side of the reel body 10, and the handle grip 22 is rotatably attached to one end of the crank arm 21 about an axis in a direction orthogonal to one end of the crank arm 21.

< reel body >

The reel body 10 has a frame 11, a right side cover 12, and a left side cover 13. The frame 11 includes a right side plate 11A and a left side plate 11B arranged at predetermined intervals, and a plurality of connecting members 11C connecting the right side plate 11A and the left side plate 11B. The right cover 12 is integrally formed with the right side plate 11A so as to cover the outer side of the right side plate 11A. The left cover 13 is fixed to the left side plate 11B so as to cover the outer side of the left side plate 11B. A space for accommodating various mechanisms described later is formed between the right side plate 11A and the right side cover 12.

The right side plate 11A and the right side cover 12 have a substantially elliptical shape that also bulges axially outward around the mounting portion of the drive gear shaft 41 (described later) as viewed from the side. The left side plate 11B and the left side cover 13 are circular in side view. The right cover 12 is detachably coupled to the right side plate 11A. The left cover 13 is detachably coupled to the left side plate 11B.

The plurality of connecting members 11C are plate-like members integrally formed with the right side plate 11A and the left side plate 11B, and connect the right side plate 11A and the left side plate 11B at three positions of the upper part, the lower part, and the rear part of the reel body 10. By providing such a coupling member 11C, even when a large load is applied to the reel body 10 and deformation such as deflection is desired, a decrease in winding efficiency is suppressed. The rod attachment portion 18 is fixed to the lower connecting member 11C, and the clutch operating member 14 is provided to the rear connecting member 11C.

The right side plate 11A rotatably supports a base end of a drive gear shaft 41 described later, which is coupled to the handle 20, and rotatably and axially movably supports a planetary gear 60 (see fig. 2) described later.

As shown in fig. 2, a spool 30 for winding a fishing line is rotatably disposed between the right side plate 11A and the left side plate 11B, a horizontal line twister mechanism 16 for uniformly winding the fishing line around the spool 30, and the clutch operating member 14.

At the center of the spool 30, a spool shaft 31 is fixed so as to pass through. The spool shaft 31 is rotatably supported by the right side plate 11A and the left side plate 11B via

bearings

32 and 33.

The clutch operating member 14 is provided to switch the clutch mechanism 50 between a clutch on state and a clutch off state for swinging around the spool shaft 31.

Here, reference symbol O in fig. 2 and the like denotes the center line of the spool shaft 31. Further, the spool axial direction is denoted by reference numeral X.

A rotation transmission mechanism 40 for transmitting torque from the handle 20 to the spool 30 and a clutch mechanism 50 provided in the rotation transmission mechanism 40 are disposed in a space between the right side plate 11A and the right side cover 12. A clutch control mechanism for controlling the clutch mechanism 50 in accordance with the operation of the clutch operation member 14, a drag mechanism, and a throwing control mechanism, which is a braking mechanism for adjusting the resistance at the time of rotation of the spool 30, are also disposed in the space between the right side plate 11A and the right side cover 12. These clutch control mechanism, drag mechanism, and throwing control mechanism are well-known structures, and therefore detailed description thereof is omitted here.

Further, a spool braking device that brakes the spool 30 by centrifugal force is disposed between the left side plate 11B and the left side cover 13. The roll brake device is a device for suppressing backlash at the time of casting.

Roll and roll shaft

As shown in fig. 2, the spool 30 has a cylindrical spool body 301 around which a fishing line is wound, a pair of left and right flange portions 302, and a shaft insertion hole 303. The flange portions 302 are provided at both ends of the spool body 301 so as to integrally protrude radially outward. The spool 30 is integrally rotatably coupled to the spool shaft 31, and the spool shaft 31 is fixedly inserted and supported by the shaft insertion hole 303.

The spool shaft 31 penetrates the right side plate 11A and extends to the outside of the right cover 12. One end 31a of the spool shaft 31 is rotatably supported by a 1 st bearing 32 housed inside the left side plate 11B. The other end 31b of the spool shaft 31 is rotatably supported by a 2 nd bearing 33 provided on the right side plate 11A. The portion of the spool shaft 31 supported by the 2 nd bearing 33 is formed to have a larger diameter than the other portion of the spool shaft 31. In this way, the spool shaft 31 is supported by bearings at two portions of the reel body 10.

The clutch portion 5 constituting the clutch mechanism 50 is provided at a penetration portion of the right side plate 11A where the spool shaft 31 penetrates. As shown in fig. 3, the clutch portion 5 includes a clutch pin 51 (engagement portion) penetrating the spool shaft 31. The clutch pin 51 is formed in a circular cross section, penetrates the spool shaft 31 in a direction orthogonal to the spool shaft, and has both ends protruding from the spool shaft 31 in the radial direction. The pin through portion 31c of the spool shaft 31 through which the clutch pin 51 passes is formed to have a large diameter similarly to the portion of the spool shaft 31 supported by the 2 nd bearing 33.

Clutch mechanism

As shown in fig. 2, the clutch mechanism 50 includes a clutch portion 5 having a clutch pin 51 and a planetary gear 60 described below. The clutch mechanism 50 can transmit and cut off rotation from the handle 20 transmitted to the spool 30 via a drive gear, not shown. The state in which the rotation from the handle 20 is transmitted to the spool 30 can be a clutch-on state, and the state in which the rotation from the handle 20 is disconnected can be a clutch-off state. The spool 30 is free to rotate in the clutch-off state, and the fishing line can be released.

< rotation transmitting mechanism >)

The rotation transmission mechanism 40 includes a function of limiting torque in a case where torque is reversely transmitted from the spool 30 to the handle 20 side. A centrifugal brake mechanism for braking the spool 30 rotatable in the wire paying-out direction is disposed in the center portion of the left side plate 11B.

The rotation transmission mechanism 40 includes a drive gear shaft 41 to which one end (right end) of the handle 20 is fixed, a drive gear (not shown) coupled to the other end (left end) of the drive gear shaft 41, and a planetary gear 60 meshed with the drive gear. The drive gear has a gear on the outer periphery and is rotatably fitted to the drive gear shaft 41. The planetary gear 60 constitutes the rotation transmission mechanism 40 and also functions as the clutch mechanism 50.

The drive gear shaft 41 is disposed parallel to the spool shaft 31, and one end side thereof is rotatably supported by the right side plate 11A. The drive gear is coupled to one end side of the drive gear shaft 41 so as to integrally rotate. In such a configuration, torque from the handle 20 is directly transmitted to the spool 30 in a state where the clutch mechanism 50 is on.

In the clutch mechanism 50, the planetary gear 60 is slid along the spool shaft 31, and an engagement groove 64, which will be described later, is engaged with the clutch pin 51, whereby a rotational force is transmitted between the spool shaft 31 and the planetary gear 60. This state is a connected state (clutch on state).

When the engagement groove 64 is disengaged from the clutch pin 51, no rotational force is transmitted between the spool shaft 31 and the planetary gear 60. This state is a cut-off state (clutch off state). In the clutch-off state, the spool 30 rotates freely.

The planetary gear 60 is biased in a direction in which the engagement groove 64 engages with the clutch pin 51, that is, in a clutch-on state, by the clutch operation member 14 disposed outside the right cover 12. Thus, the clutch operation member 14 is used to perform an on-off operation of the clutch mechanism 50.

As shown in fig. 2, the planetary gear 60 is a member made of a metal such as a stainless steel alloy or a brass alloy. The planetary gear 60 is a cylindrical member having a stepped through hole 60a (see fig. 4) through which the spool shaft 31 passes. The planetary gear 60 is rotatably supported by a bearing, not shown, and is freely movable in the spool axial direction X by the reel body 10. The planetary gear 60 is moved in the axial direction between a clutch on position close to the spool 30 and a clutch off position apart from the spool 30 compared to the clutch on position by the clutch control mechanism described above.

The planetary gear 60 has a coupling portion 61 and a support portion 62 from a 2 nd end 60c on the opposite side of the 1 st end 60b on the spool 30 side toward the right.

The coupling portion 61 is disposed between the planetary gear 60 and the support portion 62. The outer diameter of the coupling portion 61 is smaller than the diameter of the planetary gear 60.

The planetary gear 60 is rotatably supported by a bearing with respect to the right side plate 11A and is axially movable. The support portion 62 is disposed on the right side of the coupling portion 61. The support portion 62 is rotatably supported by the right cover 12 by a bearing and is axially movable. In this way, the planetary gear 60 is supported by the reel body 10 at both ends, so that the planetary gear 60 becomes difficult to tilt, and the planetary gear 60 becomes out of contact with the spool shaft 31.

As shown in fig. 3 to 7, the planetary gear 60 is formed in a disk shape coaxially provided with the spool shaft 31 at the center, and has a gear portion 65 (tooth portion) on the outer periphery.

The gear portion 65 is disposed at substantially the same position as an engagement groove 64 described later when viewed from the side in a direction orthogonal to the spool axial direction X, and is configured to be capable of meshing with a tooth portion of a drive gear.

As described above, the planetary gear 60, as shown in fig. 1, constitutes the rotation transmission mechanism 40, rotates in conjunction with the handle 20, transmits the rotation of the handle 20 to the spool 30, and also constitutes the clutch mechanism 50 that reciprocates in the spool shaft 31 direction in accordance with the operation of the clutch operation member 14.

A recess 63 is formed in the center portion on the radial inner side in the spool axial direction X in the end face of the 1 st end 60b on the spool 30 side of the planetary gear 60. The recess 63 is provided with an engagement groove 64 (engaged portion) that can be coupled to and uncoupled from the clutch pin 51 at a clutch-on position at which rotation of the handle 20 is transmitted to the spool 30.

A substantially circular convex portion 631 is formed at a central portion of the concave portion 63. The height of the boss 631 in the spool axial direction X (the height from the 1 st end 60b to the upper surface 631a of the boss 631) is smaller than the concave dimension of the concave portion 63. In the convex portion 631, stepped portions 632 are formed in two places in the circumferential direction along the circumferential direction around the spool shaft. Further, the above-described groove-like engaging groove 64 is provided in the lower step portion of the step portion 632.

The step portion 632 is provided at a position facing each other through the through hole 60a (spool shaft 31), and the upper step portion 632A and the lower step portion (engagement groove 64) are disposed counterclockwise in this order as viewed from the direction toward the 1 st end 60b in the spool axial direction X. The step 632 is set so that the width dimension in the circumferential direction of the center-side end portion in the radial direction orthogonal to the spool shaft 31 is smaller than the radius of the cross section of the clutch pin 51.

At least a part of the gear portion 65 and the engagement groove 64 overlap in the spool axial direction X.

The engagement grooves 64 are provided in a pair on a straight line along the radial direction of the spool shaft 31. The engagement groove 64 is formed in the radial direction on the end surface of the 1 st end 60b located on the bottom surface of the recess 63. The two engaging grooves 64 have a bottom portion 64a, a 1 st wall portion 64b, and a 2 nd wall portion 64c, respectively. The bottom 64a is recessed from the 1 st end 60b and disposed along the rotation direction of the planetary gear 60. The 1 st wall 64b is a wall disposed upstream of the engagement groove 64 in the wire winding direction of the planetary gear 60. The 2 nd wall 64c is a wall disposed opposite to the 1 st wall 64b on the downstream side of the engagement groove 64 in the wire winding direction of the planetary gear 60.

The 1 st wall portion 64b is formed so that, when the rotation in the wire paying-out direction from the spool 30 is transmitted by being coupled to the clutch pin 51, the planetary gear 60 is biased in a direction (clutch releasing direction) away from the spool 30 by the clutch pin 51.

Next, the operation of the dual-bearing reel 1 configured as described above will be described in detail with reference to the drawings.

As shown in fig. 3 to 5, the dual-bearing reel 1 of the present embodiment includes a clutch for switching on/off the transmission of the rotation of the handle 20 to the spool 30 via the planetary gear 60, the spool shaft 31 of the spool 30 includes a clutch pin 51, the planetary gear 60 includes a gear portion 65 and an engagement groove 64, the gear portion 65 includes a tooth portion on an outer periphery, the engagement groove 64 engages with the clutch pin 51 in an on state of the clutch in which the rotation of the handle 20 is transmitted to the spool 30, and at least a part of the gear portion 65 and the engagement groove 64 overlap in the spool axial direction X.

As a result, at least a part of the clutch pin 51 engages with the engagement groove 64 in a state of overlapping in the spool shaft 31 direction with respect to the planetary gear 60, so that the dual-bearing reel 1 can be miniaturized in the spool axial direction X.

In the present embodiment, the engagement groove 64 is disposed in the gear portion 65 of the planetary gear 60, and therefore, the end mill can be processed not by the processing of the side surface by the end mill, and therefore, a portion extending long in the spool axial direction X as in the conventional art is not required, and the dual-bearing reel 1 can be miniaturized in the spool axial direction X.

In the present embodiment, since the clutch pin 51 protrudes radially outward from the spool shaft 31 of the spool 30 and at least a part of the planetary gear 60 is engaged with the engagement groove 64 in a state of being overlapped in the spool axial direction X, the dual-bearing reel 1 can be miniaturized in the spool axial direction X.

In the present embodiment, a recess 63 recessed in the spool shaft 31 direction is formed in the center portion of the gear portion 65 on the radially inner side, and an engagement groove 64 for engaging the clutch pin 51 is provided in the recess 63.

Accordingly, the clutch pin 51 engages with the engagement groove 64 provided in the recess 63 of the gear portion 65, so that the amount of overlap in the spool axial direction X of the gear portion 65 and the engagement groove 64 can be increased, and the dual-bearing reel 1 can be more reliably miniaturized.

In the present embodiment, a stepped portion 632 is formed in the recessed portion 63 along the circumferential direction around the spool shaft, and a groove-shaped engagement groove 64 is provided at the lowermost position of the stepped portion 632.

Accordingly, since the stepped portion 632 is provided in the gear portion 65 of the planetary gear 60, the clutch pin 51 can be guided to the engagement position, i.e., the engagement groove 64, by the stepped portion 632 to be engaged.

In the present embodiment, the stepped portion 632 is provided, so that the end portion of the end mill can be used for machining.

In the present embodiment, the cross section of the clutch pin 51 is circular, and the width dimension of the step portion 632 of the recess 63 in the circumferential direction of the center-side end portion in the radial direction orthogonal to the spool shaft 31 is smaller than the radius of the cross section of the clutch pin 51.

Accordingly, the width dimension of the center side end portion of the stepped portion 632 is narrowed, so that the clutch pin 51 temporarily moved to the stepped portion 632 is not left in the stepped portion 632 and is easily dropped from the stepped portion 632 into the engaged portion 64. That is, in this case, the clutch pin 51 can be reliably guided to the engagement groove 64.

According to the dual-bearing reel 1 of the present embodiment configured as described above, the dual-bearing reel 1 can be miniaturized in the axial direction.

While embodiments of the dual bearing reel of the present invention have been described above, these embodiments are presented as examples and are not intended to limit the scope of the invention. The embodiments may be implemented in various forms, and various omissions, substitutions, and changes may be made without departing from the spirit of the invention. The embodiments and modifications thereof include, for example, substantially the same and equivalent ranges, which can be easily understood by those skilled in the art.

For example, in the present embodiment, the engagement portion is provided as the clutch pin 51 protruding radially outward from the spool shaft 31 of the spool 30, but is not limited to being provided as such a clutch pin 51.

In the present embodiment, a recess recessed in the spool axial direction X is formed in the center portion of the gear portion 65 on the radial inner side, and the engagement groove 64 for engaging the clutch pin 51 is provided in the recess 63, but the present invention is not limited thereto.

In the present embodiment, the recessed portion 63 is formed with a stepped portion 632 along the circumferential direction surrounding the spool shaft, and the engagement groove 64 is provided in the lowermost position of the stepped portion 632, but the present invention is not limited thereto.

Further, in the present embodiment, the cross section of the clutch pin 51 is circular, and the step portion 632 is set to a shape in which the width dimension in the circumferential direction of the center side end portion in the radial direction orthogonal to the spool shaft 31 is smaller than the radius of the cross section of the clutch pin 51, but the present invention is not limited thereto.

Description of the reference numerals

1. Double-bearing reel

10. Reel body

20. Handle

30. Winding drum

31. Spool shaft

40. Rotation transmission mechanism

41. Driving gear shaft

50. Clutch mechanism

51. Clutch pin (clamping part)

60. Planetary gear

63. Concave part

64. Clamping groove (clamped part)

65. Gear part

632. Step part

The X reel is axial.

Claims

1. A dual-bearing reel for transmitting rotation of a handle to a spool via a planetary gear, comprising a clutch for switching on/off of the transmission, characterized in that,

the spool shaft of the spool has an engaging portion,

the planetary gear has a gear portion and an engaged portion, the gear portion has a tooth portion on an outer periphery, the engaged portion is engaged with the engaging portion in an on state of the clutch in which rotation of the handle is transmitted to the spool,

at least a part of the tooth portion and the engaged portion overlap in the spool axial direction.

2. The dual bearing reel as claimed in claim 1, wherein,

the engagement portion is a clutch pin protruding radially outward from a spool shaft of the spool.

3. A dual bearing reel as claimed in claim 2 wherein,

a concave portion recessed on the spool shaft is formed at a central portion of the gear portion on a radial inner side thereof,

the recess is provided with the engaged portion for engaging the clutch pin.

4. The dual bearing reel as claimed in claim 3, wherein,

a step-like step portion is formed in the recessed portion in a circumferential direction around the spool shaft,

the engaged portion having a groove shape is provided at the lowermost position of the step portion.

5. The dual bearing reel as claimed in claim 4, wherein,

the cross section of the clutch pin is circular,

the step portion has a width dimension in the circumferential direction of a center-side end portion in a radial direction orthogonal to the spool shaft smaller than a radius of a cross section of the clutch pin.